Direct-acting pumping-engine



(No Model.)

7 G. DE LAVAL. DIRECT ACTING PUMPING ENGINE.

Patented May 22, 1894.

UNITED STATES PATENT OFFICE.

GEORGE DE LAVAL, OF WARREN, MASSACHUSETTS.

DIRECT-ACTING PUMPING-ENGINE.

SPECIFICATION forming part of Letters Patent No. 520,237, dated May 22,1894.

Application filed January 29, 1894.

To all whom it may concern:

Be it known that I, GEORGE DE LAVAL, a citizen of the United States, residing at Warren, in the county of Worcester and State of Massachusetts, have invented an Improvement in Direct-Acting Pumping-Engines, of which the following is a specification.

This improvement is specially adapted to duplex water pumping engines, but it is also available with air compressors and with both single and duplex pumping engines that are direct acting.

In direct acting pumping engines it is generally advantageous to employ the steam expansively, and efiorts have heretofore been made for equalizing the power exerted by combining with the engine a compensating mechanism to equalize or nearly so the power exerted throughout the entire stroke; that is to say, the steam engine acts directly upon the pump and also upon a compensating device while the pressure is maintained in the cylinder, and when the cut-oif operates and the pressure commences to decrease, the compensating mechanism acts to augment the force of the steam while the piston finishes the stroke.

My present improvements apply to pumping engines of this general character, and I combine with the cross-head of the direct acting pumping engine, toggle levers, a cylinder and fluid pressure acting upon the piston, so that when the steam pressure is acting upon the piston, piston rod and cross-head, the fluid pressure in the cylinder is augmented and becomes the resistance to the movement of the engine, and after the cut-ofi takes place the fluid pressure acting through the toggle levers compensates the loss of efficient force as the steam acts expansively, thereby equalizing the stroke and movement of the direct acting pump.

When this improvement is applied with a duplex pumping engine, the valve of one engine receives its motion in connection with the movement of the other engine; but I remark that the valve motion and valve may be of any desired character and the cut-off may be operated as usual, as these parts form no necessary portion of my present invention.

In the drawings Figure l is aside view partially in section and Fig. 2 a cross section Serial 110.4%,279. (No model.)

representing my compensating device in which the slide-block of the toggle mechan 'ism moves horizontally. Fig. 3 is a side cylinder, and B part of one end of a pump in which cylinders pistons are employed as usual that are connected by the rod or rods 0, and B is the cross-head which may be of any desired character and preferably provided with slideways E, although these may be dispensed with, and F is a cylinder in which a fluid under pressure is provided for acting upon the piston Gor plunger G, and at 2 is represented a pipe passing oft to a cylin der or other vessel containing air or gas under pressure, or to a suitable column of head for Water or other liquid under the desired pressure.

The compensating lever H, Fig. 1, is pivoted at 3 upon a suitable connection to the frame of the engine, and one end of the compensating lever H is connected to the crosshead B by a link 4, and the other end of the compensating lever H is connected to the toggle lever K that is pivoted at 5 to the piston G. It is advantageous to make the toggle lovers of about the same length between the fulcrums 3 and 5 and the joint 6 of the respective parts; and in Fig. 1 the lever K is connected at its upper end to the slide-block L in the ways M; and it will now be apparent that when the cross-head B is moved in either direction by steam acting in the cylinder A, the fluid in the cylinder F is compressed by the piston G until the centers 3, 5 and 6 come into line, which is at the half of the stroke of the piston, and during this part of the movement the power of the steam has been partially consumed in compressing the fluid in the cylinder F, and during the remainder of the stroke the expansion or pressure of the fluid in the cylinder F actsupon the piston G, and by the toggle levers H K the force is exerted in completing the movement of the cross-head B; and it is advantageous to regulate the fluid pressure acting in the cylinder F upon the piston G with reference to the steam pressure acting in the cylinder A and according to the point at which the steam is cut off, so as to equalize as nearly as possible the resistance to the movement of the steam piston during the first half of the stroke and 7 that under all circumstances the pressure exerted by the piston G is taken through the toggle portions of the levers H and K upon the pivot or rock shaft 3, so that there is but little friction upon the slide-block L, and the movement of the parts is with but little friction, and the pressure upon the piston G exerts a power in moving the cross-head Bthat is augmented toward the end of the stroke as the toggle levers approach toward a right angle to each other.

In Figs. 3 and 4, the compensating mechanism acts in the same manner as in Figs. 1 and 2, but I am enabled to dispense with the links 4 by placing the slider block L in vertical ways instead of horizontal, so that the piston rod 7 of the plunger or piston G is connected directly to the slider block L in the vertical slideways M, and with this arrangement the pivot 14 at the upper end of the compensating lever H can be connected directly to the cross-head B and at the lower end 15 directly to the slider block L, and the pivot or rock shaft 13 is provided with a link 0 forming one half of the toggle, the lower end of the link 0 being connected at 16 to the middle portion of the compensating lever H, and the operation of these parts is the same as before described with reference to Figs. 1 and 2, the lower end of the lever H and the link 0 forming the toggle and the cross shaft or pivot 13 forming the resistance to the pressure, so that the parallelism of the cross-head Bin its movement is not disturbed, and the expansive pressure acting in the cylinderF exerts the greater force near the end of the movement to compensate'or equalize the less force of the steam as itacts expansively.

By reference to Fig. 4, it will be seen that it is advantageous to employ two compensating levers H and two links 0 upon the rock shaft 13, so that the action may be equal at each side of the frame, and in this case it is more convenient to make use of only one cylinder F in which the confined pressure acts for compensating or equalizing the movemen ts of the parts.

I have preferably shown the compensating rig attached between the steam and pump cylinders, but the same can also be arranged at the end of the pump cylinder which will frame, of the piston rod 0, cross-head B, the

the stroke.

I claim as my invention l. The combination with the steam cylinder and direct acting pump and piston rods and cross head, of slides and a connecting frame between the cylinders, a piston or plunger and cylinder in which a fluid'nnder pressure acts on the piston or plunger, a compensate ing lever at one side of the frame and a link forming a toggle to compress the fluid at the middle of the stroke of the engine anda fixed pivot for the toggle on the connecting frame substantially as specified.

2. The combination with the steam cylinder and direct acting pump and piston rods and cross-head, of slides and a connecting frame between the cylinders, a piston or plunger and a cylinder in which a'flnid under preseure'acts on the piston or plunger, two separate compensating levers, one at each side of the frame and jointed at their upperendsto the cross-head, links forming with the levers toggles to compress the fluid at the middle of the engine stroke, and fixed pivots on the frame for the toggles, substantially as specified.

3. The combination with the steam cylinder A, pumping cylinder B, connecting rod 0 and cross-head B, of the compensating lever H, the link 4 connecting the upper end of the compensating lever to the cross-head, the pivot 3, the cylinder F in which a fluid under pressure is provided, the piston G, toggle lever K pivoted to the compensating lever, and the slide-block L in the slideways M, substantially as set forth.

4:. The combination with the steam cylinder, pumping cylinder, connecting-rod and cross-head, of the compensating lever, 11. connection between the upper end of the compensating lever and the cross-head, the pivot for the lever, a cylinder in which a fluid under pressure is provided, a piston therein and a toggle lever pivoted to the compensating lever, and a slide-block in the slideways, substantially as set forth.

5. The combination with the steam cylinder A, pumping cylinder B and the connecting no compensating levers H, one at each side of the connecting frame, the rock shaft forming a pivot and connecting the two levers, the compensating cylinders F and pistons G, the toggle levers K connecting the pistons Gand compensating levers H, the slide-block Land slideways M for the same, substantially as set forth.

Signed by me this 20th day of January,

cno. DE LAVAL.

Witnesses:

GEORGE P. ABORN, FRED E. 000K. 

